EP1013919B1 - Fuel injection valve - Google Patents
Fuel injection valve Download PDFInfo
- Publication number
- EP1013919B1 EP1013919B1 EP99124112A EP99124112A EP1013919B1 EP 1013919 B1 EP1013919 B1 EP 1013919B1 EP 99124112 A EP99124112 A EP 99124112A EP 99124112 A EP99124112 A EP 99124112A EP 1013919 B1 EP1013919 B1 EP 1013919B1
- Authority
- EP
- European Patent Office
- Prior art keywords
- valve
- pressure
- fuel
- diffuser
- fuel injection
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Expired - Lifetime
Links
- 239000000446 fuel Substances 0.000 title claims description 39
- 238000002347 injection Methods 0.000 title claims description 35
- 239000007924 injection Substances 0.000 title claims description 35
- 238000002485 combustion reaction Methods 0.000 claims description 4
- 238000011084 recovery Methods 0.000 claims description 4
- 238000000034 method Methods 0.000 description 5
- 230000008569 process Effects 0.000 description 5
- 230000003068 static effect Effects 0.000 description 4
- 230000008901 benefit Effects 0.000 description 2
- 230000009471 action Effects 0.000 description 1
- 238000004891 communication Methods 0.000 description 1
- 230000008602 contraction Effects 0.000 description 1
- 230000001419 dependent effect Effects 0.000 description 1
- 238000011161 development Methods 0.000 description 1
- 230000018109 developmental process Effects 0.000 description 1
- 230000000694 effects Effects 0.000 description 1
- 238000007789 sealing Methods 0.000 description 1
- 238000010025 steaming Methods 0.000 description 1
- 230000001360 synchronised effect Effects 0.000 description 1
- 230000007704 transition Effects 0.000 description 1
Images
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
- F02M47/00—Fuel-injection apparatus operated cyclically with fuel-injection valves actuated by fluid pressure
- F02M47/02—Fuel-injection apparatus operated cyclically with fuel-injection valves actuated by fluid pressure of accumulator-injector type, i.e. having fuel pressure of accumulator tending to open, and fuel pressure in other chamber tending to close, injection valves and having means for periodically releasing that closing pressure
- F02M47/027—Electrically actuated valves draining the chamber to release the closing pressure
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
- F02M63/00—Other fuel-injection apparatus having pertinent characteristics not provided for in groups F02M39/00 - F02M57/00 or F02M67/00; Details, component parts, or accessories of fuel-injection apparatus, not provided for in, or of interest apart from, the apparatus of groups F02M39/00 - F02M61/00 or F02M67/00; Combination of fuel pump with other devices, e.g. lubricating oil pump
- F02M63/0012—Valves
- F02M63/0014—Valves characterised by the valve actuating means
- F02M63/0015—Valves characterised by the valve actuating means electrical, e.g. using solenoid
- F02M63/0017—Valves characterised by the valve actuating means electrical, e.g. using solenoid using electromagnetic operating means
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
- F02M2200/00—Details of fuel-injection apparatus, not otherwise provided for
- F02M2200/04—Fuel-injection apparatus having means for avoiding effect of cavitation, e.g. erosion
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
- F02M2200/00—Details of fuel-injection apparatus, not otherwise provided for
- F02M2200/28—Details of throttles in fuel-injection apparatus
Definitions
- the invention relates to a fuel injection valve according to the preamble of the claim from as known from EP-0 690 223 A2.
- the injectors for the various Cylinder of the engine from a central high-pressure line supplied with fuel.
- low fuel consumption and quiet engine operation ensure that all injectors have the fuel exactly the same in the engine inject. This can only be guaranteed if all injectors for the exact same time at an operating point have the same opening behavior.
- Prior art electromagnetic or piezo-controlled valves which are available the actual injection valve.
- the nozzle needle moves over a control piston.
- the spool is above the pressure in the Control room moves.
- US-A-5,806,766 describes an electro-hydraulically actuable injection valve, wherein a Control piston an annular channel of a between the control piston and an actuator rod arranged control space separates, wherein between the control piston and the actuator rod a spring is arranged.
- the annular channel is also a control valve with connected to a process. If the control valve is closed when the injection valve is open, the control piston opens a connection between the annular channel and the control chamber, so that the nozzle needle is pressed onto the associated valve seat and the injection abruptly stops.
- the control valve may be designed such that the valve needle presses a ball valve into a conical seat and so opens the outlet throttle and closes.
- GB-A-2 316 447 is an injection valve for internal combustion engines with a nozzle needle, with an actuatable by means of an electromagnet directional control valve and with a Control room, which is connected to a supply line for pressurized fuel and is connected to a pressure relief line when the directional control valve is open.
- the fuel pressure acts in the control chamber via a control piston on the back End of the nozzle needle together with a nozzle needle closing spring and thus pushes the Nozzle needle on a valve seat of the injector.
- the drain designed as a throttle off the control chamber is closed with a valve ball in a conical seat.
- EP-A-0 851 115 discloses an electromagnetic metering valve for a fuel injector shown.
- the metering valve comprises a valve ball through which an outlet opening from the control chamber of the injection valve can be closed by the valve ball is pressed into a conical valve seat.
- the precision of the injection process is determined by the movement of the control piston, the pressure in the control room and thus the flow through throttles and a switching valve depends.
- the present invention is therefore based on the problem, a fuel injection valve for a high pressure injection of fuel from a central high pressure line in To provide combustion chambers, in which the opening and closing operation of the switching valve and the fuel passed through the switching valve as accurately as possible controlled becomes.
- the fuel valve according to the invention with the features of claim 1 has the Advantage that the hydraulic flow through the switching valve even at low Rail pressure and small valve lift is precisely specified. This is the flow before the switching valve specifically constricted with a specially designed throttle geometry and extended. After contraction through the throttle inlet, the fuel flow spreads in the throttle geometry according to the invention in the direction of the throttle wall from that by optimal pressure difference at the valve of the hydraulic flow increases and the opening movement of the valve ball is supported away from the valve seat.
- the flow resistance is reduced, so that it is already at a small switching valve and small rail pressure to a high Flow comes.
- the high flow leads in the inlet to the throttle to high Flow rate.
- the diameter of the diffuser is Transition to the conical seat only slightly smaller than the seat diameter. Thereby is the largest possible hydraulic cross-section of the valve when lifting the Valve ball reached.
- FIG. 1 an injector is shown.
- the fuel injection valve has a housing 2 on, which is connected to a connection 3 for the supply of injection pressure Fuel is connected from a high-pressure fuel storage, not shown.
- an injection valve needle 5 is arranged, which has a Fmmugnsabêt 6, which has a within the pressure chamber 7 lying shoulder in a smaller diameter part 9 of the injection valve needle passes.
- this one conical sealing surface 10 which cooperates with a valve seat 11 and the Injection openings 12 depending on the position of the injector needle opens or closes.
- the pressure chamber 7 is constantly connected via a pressure line 4 to the terminal 3, so that the pressure chamber 7 is constantly under high injection pressure.
- the needle 5 is controlled by the pressure piece 21 and the control piston 13.
- the spool plunges into a cylinder 14 in which it encloses a control pressure chamber 15 at the end. This is connected via a throttle bore 16 in constant communication with the terminal. 3
- the flow through the throttle bore 17 is controlled by the electric valve 19.
- the relief room is connected via a discharge nozzle 20 on the housing 2 with a return.
- the fuel injection valve described above is supplied from the high-pressure fuel storage via the terminal 3 with high pressure. This is anxious to raise in action on the shoulder 9, the fuel injection valve needle 5, so that from the pressure chamber 7 along the smaller diameter part 9 of the injection valve needle fuel to the injection ports 12 can flow and exit there. This opening counteracts the spring 18, which alone is not sufficient to keep the injector needle 5 in the pressure chamber 7 pending high fuel pressure in the closed position, but does so in the absence of high fuel pressure.
- the task of closing continues to take over the pressure in the control pressure chamber 15, which is the same when the electrically operated valve 19 is closed as the pressure in the pressure chamber 7. Due to the larger end face of the control piston 14, the closing force and the valve remains closed.
- the electrically operated valve 19 is opened, so that the pressure chamber 15 is uncoupled relieved by the throttle bore 16 and thus outweighs the opening force on the shoulder 8.
- the electrically operated valve 10 is closed again.
- Fig. 2 the two embodiments of the invention are shown in section.
- the upper part shows an embodiment with a conically extending in the flow direction to the conical seat of the ball valve 50 throttle bore 31.
- the cone angle ⁇ are designed for maximum pressure recovery in the flow.
- the lower part shows an embodiment is also generated by the conically widening in the flow direction ⁇ with the angle throttle bore 17 and two series-connected diffusers 30 and 40 maximum pressure recovery.
- the fuel flows during injection from the pressure chamber 15 into the throttle bore 17 or 31, gaining speed. At the same time it reduces static pressure in the flow. In the region of the diffuser 30, the flow is applied the wall (see the schematic representation of the fuel flow through arrows in Fig. 1) expands and is decelerated at the same time.
- the second diffuser 40 amplifies this process, causing the static pressure within the flow in Flow direction increases. This increased static pressure assists in opening of the switching valve, the movement of the valve ball 50 in the flow direction and accelerated hence the increase in fuel flow through the switching valve. simultaneously the increased fuel flow increases the cavitation tendency at the beginning of the throttle.
- the diameter of the second Diffuser 40 only slightly smaller than the diameter of the valve seat line 52 is formed.
- the throttle bore 15 slightly conically widened in the flow direction and preferably has a cone angle ⁇ up to 5 °
- the throttle bore 17, the two Diffusers 30, 40 or 31 and the valve seat 51 are aligned collinear and form a total a funnel whose wider opening is closed by the valve ball 50 or is opened.
Landscapes
- Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Fluid Mechanics (AREA)
- Electromagnetism (AREA)
- Fuel-Injection Apparatus (AREA)
Description
Die Erfindung geht von einem Kraftstoffeinspritzventil gemäß der Gattung der Patentanspruchs aus, wie es durch die EP-0 690 223 A2 bekannt ist.The invention relates to a fuel injection valve according to the preamble of the claim from as known from EP-0 690 223 A2.
Bei sogenannten Common Rail Systemen werden die Einspritzdüsen für die verschiedenen Zylinder des Motors aus einer zentralen Hochdruckleitung mit Kraftstoff versorgt. Damit möglichst niedrige Abgaswerte, niedriger Kraftstoffverbrauch und ein ruhiger Motorlauf gewährleistet sind, müssen alle Einspritzventile den Kraftstoff exakt gleich in den Motor einspritzen. Dies kann nur gewährleistet werden, wenn alle Einspritzventile zum exakt gleichen Zeitpunkt bei einem Betriebspunkt das gleiche Öffnungsverhalten besitzen.In so-called common rail systems, the injectors for the various Cylinder of the engine from a central high-pressure line supplied with fuel. In order to lowest possible emissions, low fuel consumption and quiet engine operation ensure that all injectors have the fuel exactly the same in the engine inject. This can only be guaranteed if all injectors for the exact same time at an operating point have the same opening behavior.
Zur genauen Steuerung des Einspritzvorganges mit Common Rail Systemen sind daher im Stand der Technik elektromagnetische oder piezogesteuerte Ventile bekannt, die sich vor dem eigentlichen Einspritzventil befinden. Bei einem solchen Kraftstoffeinspritzventil wird die Düsennadel über einen Steuerkolben bewegt. Der Steuerkolben wird über den Druck im Steuerraum bewegt.For precise control of the injection process with common rail systems are therefore in Prior art electromagnetic or piezo-controlled valves are known which are available the actual injection valve. In such a fuel injection valve is the nozzle needle moves over a control piston. The spool is above the pressure in the Control room moves.
US-A-5,806,766 beschreibt ein elektrohydraulisch betätigbares Einspritzventil, bei dem ein Steuerkolben einen Ringkanal von einem zwischen dem Steuerkolben und einer Aktuatorstange angeordneten Steuerraum trennt, wobei zwischen dem Steuerkolben und der Aktuatorstange eine Feder angeordnet ist. Der Ringkanal ist zudem über ein Steuerventil mit einem Ablauf verbunden. Wird bei geöffnetem Einspritzventil das Steuerventil geschlossen, so öffnet der Steuerkolben eine Verbindung zwischen dem Ringkanal und dem Steuerraum, so dass die Düsennadel auf den zugeordneten Ventilsitz gepresst wird und die Einspritzung abrupt stoppt. Hierbei kann das Steuerventil so ausgebildet sein, dass die Ventilnadel eine Ventilkugel in einen konischen Sitz presst und so die Auslaufdrossel öffnet und schließt.US-A-5,806,766 describes an electro-hydraulically actuable injection valve, wherein a Control piston an annular channel of a between the control piston and an actuator rod arranged control space separates, wherein between the control piston and the actuator rod a spring is arranged. The annular channel is also a control valve with connected to a process. If the control valve is closed when the injection valve is open, the control piston opens a connection between the annular channel and the control chamber, so that the nozzle needle is pressed onto the associated valve seat and the injection abruptly stops. In this case, the control valve may be designed such that the valve needle presses a ball valve into a conical seat and so opens the outlet throttle and closes.
In GB-A-2 316 447 ist ein Einspritzventil für Verbrennungskraftmaschinen mit einer Düsennadel, mit einem mittels eines Elektromagneten betätigbaren Wegeventil und mit einem Steuerraum, der mit einer Zuleitung für unter Druck stehenden Brennstoff verbunden ist und bei geöffnetem Wegeventil mit einer Druckentlastungsleitung verbunden ist, dargestellt. Der Brennstoffdruck wirkt im Steuerraum über einen Steuerkolben auf das rückseitige Ende der Düsennadel zusammen mit einer Düsennadelschließfeder und drückt damit die Düsennadel auf ein Ventilsitz des Einspritzventils. Der als Drossel ausgebildete Ablauf aus dem Steuerraum ist mit einer Ventilkugel in einem konischen Sitz verschließbar.In GB-A-2 316 447 is an injection valve for internal combustion engines with a nozzle needle, with an actuatable by means of an electromagnet directional control valve and with a Control room, which is connected to a supply line for pressurized fuel and is connected to a pressure relief line when the directional control valve is open. The fuel pressure acts in the control chamber via a control piston on the back End of the nozzle needle together with a nozzle needle closing spring and thus pushes the Nozzle needle on a valve seat of the injector. The drain designed as a throttle off the control chamber is closed with a valve ball in a conical seat.
In EP-A- 0 851 115 ist ein elektromagnetisches Dosierventil für ein Kraftstoffeinspritzventil dargestellt. Das Dosierventil umfasst eine Ventilkugel, durch die eine Auslassöffnung aus dem Steuerraum des Einspritzventils verschlossen werden kann, indem die Ventilkugel in einen konisch ausgebildeten Ventilsitz gepresst wird.EP-A-0 851 115 discloses an electromagnetic metering valve for a fuel injector shown. The metering valve comprises a valve ball through which an outlet opening from the control chamber of the injection valve can be closed by the valve ball is pressed into a conical valve seat.
Die Präzision des Einspritzvorganges wird von der Bewegung des Steuerkolbens bestimmt, die vom Druck im Steuerraum und damit vom Durchfluss durch Drosseln und ein Schaltventil abhängt.The precision of the injection process is determined by the movement of the control piston, the pressure in the control room and thus the flow through throttles and a switching valve depends.
Der vorliegenden Erfindung liegt daher das Problem zugrunde, ein Kraftstoffeinspritzventil für eine Hochdruckeinspritzung von Kraftstoff aus einer zentralen Hochdruckleitung in Brennräume zu schaffen, bei welchem der Öffnungs- und Schließvorgang des Schaltventils und der durchgeflossene Kraftstoff durch das Schaltventil möglichst genau kontrollierbar wird. The present invention is therefore based on the problem, a fuel injection valve for a high pressure injection of fuel from a central high pressure line in To provide combustion chambers, in which the opening and closing operation of the switching valve and the fuel passed through the switching valve as accurately as possible controlled becomes.
Das erfindungsgemäße Kraftstoffventil mit den Merkmalen des Anspruchs 1 hat den Vorteil, daß der hydraulische Durchfluß durch das Schaltventil auch bei niedrigem Raildruck und kleinem Ventilhub genau vorgebbar ist. Dazu wird die Strömung vor dem Schaltventil mit einer speziell gestalteten Drosselgeometrie gezielt eingeschnürt und erweitert. Nach der Kontraktion durch den Drosseleinlauf breitet sich die Kraftstoffströmung bei der erfindungsgemäßen Drosselgeometrie so in Richtung der Drosselwand aus, daß durch optimale Druckdifferenz am Ventil der hydraulische Durchfluß erhöht und die Öffnungsbewegung der Ventilkugel vom Ventilsitz weg unterstützt wird.The fuel valve according to the invention with the features of claim 1 has the Advantage that the hydraulic flow through the switching valve even at low Rail pressure and small valve lift is precisely specified. This is the flow before the switching valve specifically constricted with a specially designed throttle geometry and extended. After contraction through the throttle inlet, the fuel flow spreads in the throttle geometry according to the invention in the direction of the throttle wall from that by optimal pressure difference at the valve of the hydraulic flow increases and the opening movement of the valve ball is supported away from the valve seat.
Durch die vorteilhafte Ausführung der Drossel wird der Strömungswiderstand herabgesetzt, so daß es schon bei kleinem Schaltventilhub und kleinem Raildruck zu einem hohen Durchfluß kommt. Der hohe Durchfluß führt im Einlauf in die Drossel zu hoher Strömungsgeschwindigkeit.Due to the advantageous embodiment of the throttle, the flow resistance is reduced, so that it is already at a small switching valve and small rail pressure to a high Flow comes. The high flow leads in the inlet to the throttle to high Flow rate.
Deshalb fällt dort der statische Druck bis auf den Dampfdruck des Kraftstoffes ab, und es kommt zu Dampfbildung, d.h. Kavitation. Durch diesen Effekt, der mit der erfindungsgemäßen Drosselgeometrie bei möglichst kleinen Raildrücken und Schaltventilhüben eintritt, ist der hydraulische Durchfluß nur noch vom Druck vor der Drossel und der Einlaufgeometrie bestimmt (bei konstanter Kraftstofftemperatur und konstantem Kraftstofftyp) und ist unabhängig vom Ventilhub. Aufgrund des definierten hydraulischen Durchflusses wird der über die entsprechenden Schaltventile elektronisch gesteuerte Einspritzbeginn mehrerer Einspritzdüsen, die von einer gemeinsamen Hochdruckleitung versorgt werden, zuverlässig synchronisiert. Therefore, there the static pressure drops down to the vapor pressure of the fuel, and it comes to steaming, i. Cavitation. By this effect, with the inventive Throttle geometry with the smallest possible rail pressures and switching valve strokes occurs, the hydraulic flow is only from the pressure before the throttle and the inlet geometry determined (at constant fuel temperature and constant Fuel type) and is independent of the valve lift. Due to the defined hydraulic Flow is the electronically controlled via the corresponding switching valves Start of injection of several injectors, from a common high pressure line be supplied, reliably synchronized.
In den abhängigen Ansprüchen aufgeführte Maßnahmen definieren vorteilhafte Weiterbildungen und Verbesserungen des in Anspruch 1 angegebenen Kraftstoffeinspritzventils.Measures listed in the dependent claims define advantageous developments and improvements of claim 1 fuel injection valve.
Gemäß einer bevorzugten Ausführungsform ist der Durchmesser des Diffusors beim Übergang in den Kegelsitz nur geringfügig kleiner als der Sitzdurchmesser. Dadurch wird ein möglichst großer hydraulischer Querschnitt des Ventils beim Abheben der Ventilkugel erreicht.According to a preferred embodiment, the diameter of the diffuser is Transition to the conical seat only slightly smaller than the seat diameter. Thereby is the largest possible hydraulic cross-section of the valve when lifting the Valve ball reached.
Die Erfindung ist anhand von Fig. 1 und 2 näher erläutert. Es zeigen:
- Fig. 1:
- eine Schnittansicht eines gesamten Common Rail Injektors; und
- Fig. 2
- die beiden Ausführungsformen der Erfindung.
- Fig. 1:
- a sectional view of an entire common rail injector; and
- Fig. 2
- the two embodiments of the invention.
In Fig. 1 ist ein Injektor dargestellt. Das Kraftstoffeinspritzventil weist ein Gehäuse 2
auf, das mit einem Anschluß 3 zur Zuführung von auf Einspritzdruck gebrachtem
Kraftstoff aus einem nicht weiter gezeigten Kraftstoffhochdruckspeicher verbunden ist.
In dem Gehäuse 2 des Kraftstoffeinspritzventils ist eine Einspritzventilnadel 5 angeordnet,
die einen Führugnsabschnitt 6 aufweist, der über eine innerhalb des Druckraumes
7 liegende Schulter in einem im Durchmesser kleineren Teils 9 der Einspritzventilnadel
übergeht. Am Ende dieses im Durchmesser kleineren Teils 9 weist dieser eine
konisch Dichtfläche 10 auf, die mit einem Ventilsitz 11 zusammenwirkt und dabei die
Einspritzöffnungen 12 je nach Stellung der Einspritzventilnadel öffnet oder schließt.In Fig. 1, an injector is shown. The fuel injection valve has a
Der Druckraum 7 ist über eine Druckleitung 4 ständig mit dem Anschluß 3 verbunden,
so daß der Druckraum 7 ständig unter hohem Einspritzdruck steht. Die Nadel 5 wird
über das Druckstück 21 und den Steuerkolben 13 gesteuert. Der Steuerkolben taucht in
einen Zylinder 14 ein, in dem er stimseitig einen Steuerdruckraum 15 einschließt. Dieser
steht über eine Drosselbohrung 16 in ständiger Verbindung mit dem Anschluß 3.
Weiterhin führt vom Steuerdruckraum 15 eine Drosselbohrung 17 ab, deren Austritt
über ein elektrisches Ventil 19 in einen Entlastungsraum 18 mündet. Der Durchfluß
durch die Drosselbohrung 17 wird über das elektrische Ventil 19 gesteuert. Der Entlastungsraum
ist über einen Ablaufstutzen 20 am Gehäuse 2 mit einem Rücklauf verbunden.The
Im Betrieb wird das oben beschriebenen Kraftstoffeinspritzventil von dem Kraftstoffhochdruckspeicher
über den Anschluß 3 mit Hochdruck versorgt. Dieser ist bestrebt, in
Einwirkung auf die Schulter 9 die Kraftstoffeinspritzventilnadel 5 anzuheben, so daß
aus dem Druckraum 7 entlang des im Durchmesser kleineren Teils 9 der Einspritzventilnadel
Kraftstoff zu den Einspritzöffnungen 12 fließen und dort austreten kann. Diesem
Öffnen wirkt die Feder 18 entgegen, die allein jedoch nicht ausreicht, die Einspritzventilnadel
5 bei im Druckraum 7 anstehenden Kraftstoffhochdruck in Schließstellung
zu halten, dies aber bei fehlendem Kraftstoffhochdruck tut. Die Aufgabe des
Schließens übernimmt weiterhin der Druck im Steuerdruckraum 15, der bei geschlossenem
elektrisch betätigten Ventil 19 gleich ist wie der Druck im Druckraum 7. Aufgrund
der größeren Stirnfläche des Steuerkolbens 14 überwiegt die Schließkraft und
das Ventil bleibt geschlossen. Zur Auslösung der Einspritzung wird das elektrisch betätigte
Ventil 19 geöffnet, so daß der Druckraum 15 abgekoppelt durch die Drosselbohrung
16 entlastet wird und somit die Öffnungskraft auf die Schulter 8 überwiegt. Zur
Beendigung des Einspritzvorgangs wird das elektrisch betätigte Ventil 10 wieder geschlossen.
In Fig. 2 sind die beiden Ausführungsformen der Erfindung im Schnitt gezeigt. Der
obere Teil zeigt eine Ausführungsform mit einer sich in Strömungsrichtung konisch bis
zum Kegelsitz des Kugelventils 50 erweiternden Drosselbohrung 31. Die Konuswinkel
α werden auf maximalen Druckrückgewinn in der Strömung ausgelegt. Der untere Teil
zeigt eine Ausführungsform bei ebenfalls durch die sich in Strömungsrichtung konisch
mit dem Winkel α erweiternde Drosselbohrung 17 und zwei in Reihe geschaltene Diffusoren
30 und 40 maximaler Druckrückgewinn erzeugt wird.In operation, the fuel injection valve described above is supplied from the high-pressure fuel storage via the
In Fig. 2, the two embodiments of the invention are shown in section. The upper part shows an embodiment with a conically extending in the flow direction to the conical seat of the
Der Kraftstoff strömt beim Einspritzen aus dem Druckraum 15 in die Drosselbohrung
17 oder 31 und gewinnt dabei an Geschwindigkeit. Gleichzeitig verringert sich der
statische Druck in der Strömung. Im Bereich des Diffusors 30 liegt die Strömung an
der Wandung an (vergl. schematische Darstellung der Kraftstoffströmung durch Pfeile
in Fig. 1), weitet sich auf und wird gleichzeitig abgebremst. Der zweite Diffusor 40
verstärkt diesen Vorgang, wodurch der statische Druck innerhalb der Strömung in
Strömungsrichtung ansteigt. Dieser erhöhte statische Druck unterstützt beim Öffnen
des Schaltventils die Bewegung der Ventilkugel 50 in Strömungsrichtung und beschleunigt
daher die Zunahme des Kraftstoffflusses durch das Schaltventil. Gleichzeitig
verstärkt der erhöhte Kraftstoffluß die Kavitationsneigung am Anfang der Drossel.The fuel flows during injection from the
Gemäß einer besonders bevorzugten Ausführungsform ist der Durchmesser des zweiten
Diffusors 40 nur geringfügig kleiner als der Durchmesser der Ventilsitzlinie 52 ausgebildet.
Dadurch wird bei einer Bewegung der Ventilkugel 50 in Strömungsrichtung
(vergl. Doppelpfeil in Fig. 1) ein maximaler Durchflußquerschnitt freigegeben.According to a particularly preferred embodiment, the diameter of the
Zur weiteren Verstärkung der Druckrückgewinnung und der Kavitationsneigung ist bevorzugt ferner die Drosselbohrung 15 leicht konisch in Strömungsrichtung erweitert und weist vorzugsweise einen Konuswinkel α bis zu 5° aufTo further enhance the pressure recovery and cavitation tendency is preferred Furthermore, the throttle bore 15 slightly conically widened in the flow direction and preferably has a cone angle α up to 5 °
Wie aus der Figur 1 deutlich zu erkennen ist, sind die Drosselbohrung 17, die beiden
Diffusoren 30, 40 oder 31 und der Ventilsitz 51 kollinear ausgerichtet und bilden insgesamt
einen Trichter, dessen breitere Öffnung durch die Ventilkugel 50 verschlossen
bzw. geöffnet wird.As can be seen clearly from Figure 1, the throttle bore 17, the two
Claims (5)
- Fuel injection valve for high-pressure injection of fuel from a central high-pressure line into combustion chambers in an internal combustion engine, which has a switching valve (19) with a conical valve seat (51) and a valve ball (50), with the valve ball (50) being raised off the conical valve seat (51) in the open state, which is fed via a throttle bore (17, 31) from a pressure area (15) which is operatively connected to a central high-pressure line, characterized in that the throttle bore (17, 31) is in the form of a diffuser, which widens in the form of a funnel towards the valve seat (51) between the throttle inlet on the pressure area (15) and the conical valve seat (51), such that the fuel flow essentially follows the wall of the throttle bore (17, 31).
- Fuel injection valve according to Claim 1, characterized in that the diffuser is in the form of a conical diffuser (31), a step diffuser (30, 40) or a combination of the two.
- Fuel injection valve according to Claim 1 or 2, characterized in that the diameter at the junction to the conical valve seat (51) is preferably only slightly less than the seat diameter (52).
- Fuel injection valve according to one of Claims 1 to 3, characterized in that the diffuser is designed such that the flow follows the wall, and as high a pressure recovery as possible can be achieved.
- Fuel injection valve according to one of Claims 1 to 4, characterized in that the throttle bore (17, 31), the entire diffuser and the valve seat (51) form a funnel, with respect to whose central opening the valve ball can move.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| DE19859537A DE19859537A1 (en) | 1998-12-22 | 1998-12-22 | Fuel injector |
| DE19859537 | 1998-12-22 |
Publications (3)
| Publication Number | Publication Date |
|---|---|
| EP1013919A2 EP1013919A2 (en) | 2000-06-28 |
| EP1013919A3 EP1013919A3 (en) | 2002-02-13 |
| EP1013919B1 true EP1013919B1 (en) | 2004-10-20 |
Family
ID=7892302
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| EP99124112A Expired - Lifetime EP1013919B1 (en) | 1998-12-22 | 1999-12-02 | Fuel injection valve |
Country Status (4)
| Country | Link |
|---|---|
| US (1) | US6276335B1 (en) |
| EP (1) | EP1013919B1 (en) |
| JP (1) | JP2000186647A (en) |
| DE (2) | DE19859537A1 (en) |
Families Citing this family (14)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE10007175B9 (en) * | 2000-02-17 | 2004-11-04 | Siemens Ag | Injection valve for injecting fuel into an internal combustion engine |
| DE10039215A1 (en) * | 2000-08-11 | 2002-02-28 | Bosch Gmbh Robert | Seat valve arrangement, in particular for a fuel injection system of an internal combustion engine |
| JP2003113761A (en) | 2001-08-01 | 2003-04-18 | Denso Corp | Fuel injection valve |
| DE10152173A1 (en) * | 2001-10-23 | 2003-04-30 | Bosch Gmbh Robert | Solenoid valve for controlling an injection valve |
| US7111614B1 (en) | 2005-08-29 | 2006-09-26 | Caterpillar Inc. | Single fluid injector with rate shaping capability |
| DE102006034111A1 (en) * | 2006-07-24 | 2008-01-31 | Robert Bosch Gmbh | Servo-valve-controlled injector for injecting fuel into cylinder combustion chambers of internal combustion engines; in particular common rail injector |
| DE102007004553A1 (en) * | 2007-01-30 | 2008-07-31 | Robert Bosch Gmbh | Ball seat valve for use in injecting device, has diffuser arranged between choke valve and valve seat, and side turned towards seat is provided with narrowing that includes narrowing section turned away from seat |
| DE102008044096A1 (en) * | 2008-11-27 | 2010-06-02 | Robert Bosch Gmbh | Method for producing throttle bores with a low caviation transfer point |
| DE102009028943A1 (en) * | 2009-08-27 | 2011-03-03 | Robert Bosch Gmbh | Cavitation erosion-optimized ball seat valve |
| JP5051279B2 (en) * | 2009-12-21 | 2012-10-17 | 株式会社デンソー | Constant residual pressure valve |
| DE102010063981A1 (en) * | 2010-12-22 | 2012-06-28 | Continental Automotive Gmbh | Magnetodynamic actuator and method for actuating a fuel injection valve |
| DE102013214589A1 (en) * | 2013-07-25 | 2015-01-29 | Robert Bosch Gmbh | Switching valve for a fuel injector |
| DE102015204255A1 (en) * | 2015-03-10 | 2016-09-15 | Robert Bosch Gmbh | Fuel injector for a fuel injection system |
| FR3055370B1 (en) * | 2016-09-01 | 2020-05-01 | Delphi Technologies Ip Limited | COIL ASSEMBLY |
Family Cites Families (11)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| IT1250900B (en) * | 1991-12-24 | 1995-04-21 | Elasis Sistema Ricerca Fiat | ELECTROMAGNETICALLY OPERATED FUEL INJECTION VALVE. |
| CH689282A5 (en) * | 1994-03-29 | 1999-01-29 | Christian Dipl-Ing Eth Mathis | Injection valve for a particular intended as a diesel engine internal combustion engine. |
| IT232490Y1 (en) * | 1994-07-01 | 2000-01-10 | Elasis Sistema Ricerca Fiat | BLOCK TRAVEL ADJUSTMENT DEVICE FOR A FUEL INJECTOR |
| EP0745764B1 (en) * | 1995-06-02 | 2001-03-21 | Ganser-Hydromag Ag | Fuel injection valve for internal combustion engines |
| DE19618468C1 (en) * | 1996-05-08 | 1997-04-30 | Siemens Ag | Hydraulically actuated fuel injection valve for combustion engine |
| DE19624001A1 (en) * | 1996-06-15 | 1997-12-18 | Bosch Gmbh Robert | Fuel injection device for internal combustion engines |
| DE19634105A1 (en) * | 1996-08-23 | 1998-01-15 | Daimler Benz Ag | Injection valve for internal combustion engines |
| IT1289795B1 (en) * | 1996-12-23 | 1998-10-16 | Elasis Sistema Ricerca Fiat | IMPROVEMENTS TO AN ELECTROMAGNETICALLY OPERATED DOSING VALVE, WITH BALL SHUTTER, FOR A FUEL INJECTOR. |
| US5890653A (en) * | 1998-04-23 | 1999-04-06 | Stanadyne Automotive Corp. | Sensing and control methods and apparatus for common rail injectors |
| DE19822503C1 (en) * | 1998-05-19 | 1999-11-25 | Siemens Ag | Control valve for fuel injector |
| JP3704957B2 (en) * | 1998-07-06 | 2005-10-12 | いすゞ自動車株式会社 | Injector |
-
1998
- 1998-12-22 DE DE19859537A patent/DE19859537A1/en not_active Ceased
-
1999
- 1999-12-02 DE DE59910896T patent/DE59910896D1/en not_active Expired - Lifetime
- 1999-12-02 EP EP99124112A patent/EP1013919B1/en not_active Expired - Lifetime
- 1999-12-17 US US09/465,843 patent/US6276335B1/en not_active Expired - Fee Related
- 1999-12-22 JP JP11365139A patent/JP2000186647A/en active Pending
Also Published As
| Publication number | Publication date |
|---|---|
| DE19859537A1 (en) | 2000-07-06 |
| EP1013919A3 (en) | 2002-02-13 |
| DE59910896D1 (en) | 2004-11-25 |
| JP2000186647A (en) | 2000-07-04 |
| EP1013919A2 (en) | 2000-06-28 |
| US6276335B1 (en) | 2001-08-21 |
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